Warp-beam-driven letoff for textile looms



Aug. 16, 1949. c. H. WILLIAMS WARP-BEAM-DRIVEN LET-OFF FOR TEXTILE L QOMS 4 Sheets-Sheet 2 Filed Aug. 15, 194e Aug. 16, 1949.r

c. H. WILLIAMS 2,479,285 WARP-BEAM-DRIVEN LET-OFF FOR TEXTILE LOOMS Filed Aug: 15, 1946 4 Sheets-Sheet 5y IN VEN TOR.

Aug. 16, 1949.

Filed Aug. 15, 194e C. H. WILLIAMS WARP-BEAM-DRVEN LET-OFF FOR TEXTILE LOOMS l 4 Sheets-Sheet 4 l INVENTOR. CZ/O/V Af PWM/241145 Patented Aug. 16, 1949 WARP-BEAM-DRIVEN LETOFF FOR TEXTILE LooMs Charlton-Hudson Williams,v Columbus, Ga., assignor to Swift Manufacturing Company, Columbus, Ga., a corporation of Georgia `,Application August 13, 1946, Serial No. 690,098 Y The present invention relates to improvements in Warp-beam-driven let-on for textile looms.

While there are a great manyproposals in the prior art for regulating the delivery of the warp from the warp beam, only the Roper and the Draper mechanisms have had any success in actual practice, and it is well known that both such prior mechanisms employ the principle of driving the warp beam from the let-off, the motion originating in the lay sword or some external mechanism of the loom. The difficulty Ywith such principle lies in the mechanical dii-liculty of driving the large and heavy warp beam from the relatively small let-oil mechanism which must be sensitive to perform its function correctly, and therefore in the old types of let-offs these delicate' parts were subject to undue stresses particularly when employed with a warp beam of large diameter in excess of the dimensions for Which the loom and the let-off were originally designed for maximum eciency, the precision of the let-olf and its general eicacy suffering under such circumstances.

Another diicultyexperienced with the prior mechanisms was that a change in the rate of picks per inch necessitated a gear-ratio change in the pinion ofV the let-oir driving the warp beam gear, as a result of which a number of gears of different ratios were required at considerable expense and investment to be kefpt on hand in the mill adjacent to the loom for substitution along with pick changes. This involved also considerable additional expense in the labor of changing these pinions and of the loss of time in loom operation.

An object of the present invention is to obviate the diiiiculties above enumerated by reversing the direction of movement so that according to the present invention the warp beam is driven in the usual manner by the tension and draft of the Warp and it imparts motion to the let-01T under circumstances as controlled by the inherent action of the let-ofi` which is generally of that type known inthe art as friction let-oils.

A further diiculty encountered withV the prior mechanisms involved the large bulk, the relatively numerous yparts and the rather complicated motions of the same, all of which adversely affected the proper maintenance and proper operations of the let-on due to the high humidity conditions prevailing in the Weaving rooms of textile mills which has always resulted in the deposit Yof heavy moisture and lint upon the mechanisms to the disastrous extent of impairing their oorr recttandV proper operation. Y It isafurther object of the invention to sim- Claims. (Cl. 139-107) plify the construction of let-offs andthe-operation thereof and to not only reduce the number of parts but to coordinate such parts into a more compact and more easily lubricated mechanism and one less affected .by the moisture-matted lint which is bound to settle on all mechanisms in the weaving rooms. Y

A still further object of the present invention resides in the fact that the Weaver may easily let back the warp beam when picking out a defect owing to the fact that the warp beam drivesrthe let-or and is entirely free of any compulsion from the let-oil'. v Y

A further diiiiculty with the prior mechanism is that the let-off motions degenerate into jerky and uneven movements in the production of goods having fewer picks per'inch, andY this lack of uniform smooth motion is communicated to the warp beam because of the let-off drive of the same and results in a lesser proportion'of rstgrade materials and increases production of second-grade materials.

It is a still further object of the yinvention to provide-an improved let-off motion that is uniformly smooth at all rates of operation to the end that greater uniformity in the production of goods of first class is had with very few seconds.

A still further object of the invention is to provide an improved let-01T which admitsof adjustment by the simple expedient of rotating a wing nut and does not'require the attention of an experienced loom xer or operator.

A still further object of the .invention is to provide an improved let-off that isfunaflected by climatic conditions and lin which little orv no lubrication is required owing to the simplicity of the construction and in which the let-off requires a bare minimum of attention as contrasted with the considerable maintenancerequired by prior art machines..

With the foregoing and other objects in View, the invention'will be described more fully hereinafter and more particularly pointed out in the appended claims.

In the drawings, in Whichpthe same reference characters are used tov denote the same Vparts throughout the several views:

Figure 1 is a fragmentary side elevational view of .a Draper'loomvfrom the left-hand side, shovving incorporated therein'a let-off mechanism constructed in'accordance with the invention.

Figure 2'is a top plan view of the same.

`Figure 3 is a .vertical sectiontaken on theline 3-3inFigure1'. .a s s. j s Y t V.support employed.

'tension regulating plate employed.

Figure 4 is a fragmentary vertical section taken on the line 4-4 in Figure 2.

Figure 5 is a similar view 5-5 in Figure 2.

Figure 6 is a vertical section of the brake drum and ratchet assembly taken on the line 6-6 in Figurel. 1 vY Figurev 'l 'is a vertical-section taken on the line '|-1 in Figure 3.

Figure 8 is a side elevational View drum and ratchet assembly with the Ybeam arm in the raised starting position.

Figure 9 is a similar view showing the beam arm lowered to the flnisl'ipositlon withconsequent automatic readjustfnentof the friction brake.

Figure 10 is a perspective .fview `ofthe tension shaft bearing.

taken on the line Figure 11 is a perspective view of the ratchet shaft bearing. v 'Figure 112is a=iperspeetive Iview `of the tension 'support armfand :its pivotal bearing.

Figure /13 Y' is a perspective'. vewriof .the let-off idriving pinion.

Figurellfi is aperspectivelview 'of a..spacecollar i employed.

Figure 15 is a perspective View of, the ratchet shaft.

Figure 16v isY a .perspective view of the friction drum andratchetrassembly. Y

`Figure 17 is av-perspective view of a type of beam arm employed.

Figure 18 is a side elevational viewof a modille'd form of let-coifc'ons'tructed.in accordance with thepresentinventien andapplicable to a Crompton 8a Knowles C-4 loom.

A Figure 19 is acvertical'section taken on the .line

Figure 20 is aside elevation of a `form of ratchet shaft bearing` as vfound on the C44 loom.

' Figure21 is a top fplan view of the same.

Figure 22 is a top yplan view of a form of friction strap retainer as employed on the C-4 loom.

= Figure 23 isa top planv view of a tension rod Figure24 is a fragmentary perspective View of a form of friction strapemployed.

Figure 25^is atop plan `view of a form of tension rod as employed on-the C'4 loom.

Figure--26 is asideelevational view of a further l.'

modified forniof the invention as applicable to a Crompton 8a Knowles C- 2 loom.

Figures 27 is a v ertical section taken onthe line 21-21 in Figure 26.

Figure 28 is a side elevation of a form of Y ratchetshaft bearing 'employed according to the invention` onthe C-2.loom. Figure 2 9 is a top plan view` ofthe Same. Figure 30 is a side elevational View ofA a form of journaling a ratchet sha-H33. A ratchet' shaft pinion 34 is keyed t''the ratchet v'shaft k33 and meshes with-the bearn'lge'ar 35.1 the outer side Yof the loom side I3| is africti'onflrum 3`6,..and

within the friction `dr'um- 36 is :arat'chet gear 31. Within the friction drum -36`raretwoipa`wis 46 and 41 located diametrically opposite oneanotherand engagingthe'ratchetrgear 31.; "IT-he 'ratchet gear 3l is rigidly affixed to the ratchet slfaftl 33- by.'

of the brake l means of a set screw 38. The ratchet shaft pinion 34 is kept in mesh with the beam gear 35 by means of a collar 39, rigidly aixed to the shaft 33 by means of a set screw 4D.

The friction drum 36 is kept at a suitable distance from the ratchet shaft bearing 32 by means of a tubular spacer 4l. llvlunted at a suitable distance forwardly ofltherat'chet shaft bearing 32 is a tension shaft bearing 42 for carrying i-a tension shaft 43. On the inner or loom side ofthetension vshaft 43 at a point substantially to the end of the tension shaft 43 is rigidly Yclose aixed a beam arm 44 which is held rigidly in Y place-to the tensoni'shaft 43 by means of a set screw 45.

vOutwanrrilyof'the loom side 3|, a tension supg port arm 48 is affixed to the tension shaft 43 by a set screw 49. On the upper end of the tension support `arm 48 is mounted a stud or pivot 50 on which rotates a pivotal bearing 5|. The bearing 5|' slidablysupports` a tension1rodz52.. One endof the tensionr'od 52 .carries ahook. 53, the other end ibeing threaded to :receive a; wingY nut 54. A1 helical spring :55 envelopstheptension.rod V25 :.52, one end of said spring .abutting :thejpivotal bearing 5| and theother end'ofsaidspring abut- .ting the wing nut 54.

A frictionfstrapSii,` having `perk or other brake :friction block spacers 59 and loopedrendsf51 and A58, is Vplaced about thefrictiondrum 36. i ,One of theV looped ends 5l tisslpped over the tension shaft 43 and the other-looped1end56 engages jthe hook53 on the tension rodz52.

In operation ofthe improvedllet-i-.oifas applied Vto the Draper loom, the replenished'warp beam 6e is replacedv as usual in the loom Ain a manner to mesh the beamr gear 35 withfthe 4ratchet shaft pinion 34; thisbeing accomplished -by mounting the warp beam '60 in its bearings in the usual manner.

Initially, the setscrews andv49 `are loosened, and the beam arm 44 is adjust'edangularly about the aXis of the Vtension shaft- 43 without impart- Ying any rotation-to thisshaftthe adjustment being countereclockwise to a-point where the foot v62 rides upon the external peripheryzof thewarp mass 6| on the warpbeam 6G. At this point the set screw 45 is retightened toiafxthefbeamarm r44-to the-tension shaft.43. Y

. Thetension support arrn48, which is stillloose on thetension shaft 43 is now'rotated'or adjusted in a clockwise direction, asviewed in Figures 1,

8, and 9, through an angular distance whichV will cor-respond` yto' the amount of tension, roughly .55,valued, desired lto be placedupon the brake band 6 in its embrace of the brake drum 36. The second set screw49 is thereupon -retightened to cause .-the tension support arm 48 torotate with the ten- Vsion shaft 43.

The third step involvesv rotation of the wing nut 54m a right-hand direction to cause the same to-axially approach 4the pivotal-bearingrEl which now acts as V a fixed abutment against whichv the Y.coil springl 55 maybe Athus compressed. There- -5factiongof the coilrspringfrorn the fixed abutment -5| against adjusting abutmentornut 54 `tends --to slidethe tension rod 52 through the pivotal bear'ing |l rin a .right-hand direction, viewed in Figures l, Sand-9.l This further draws taut the brake band-56-about the brake drum 36 and `adds 1 to the ten-sion of thelet-oif. The'fadjustment-of 1 the nut-54 inthe-threaded endportion'of the ten- --sion rodi 52 therefore constitutes 5a vsecondary or Vernier adjustment ontheefizi'ctionybrakeof vthe leteof aime-manner in which this fadustment is amaze@ actually accomplishedis to set thebeam'arm 44,-`

then to set the tension support arm 48, following which the loom is started and the let-ofi' Iof the warp from the warp beam 60 is observedV as to the freeness, smoothness and evenness ofits delivery from the warp beam asl demanded by the number of picks per inch in the weaving operation. VAs the loomy is Ythus preliminarily and empirically operated under observation, the Wing nut 54 is.

rotated in one direction orthe other to increase or decrease'thecompression of the coil spring 55 ,and thereby correspondingly adjust the fric-l tional tension of the brake band 56 on the brake drum 36. In this way a micrometeradjustment of the frictional brake tension is nicely secured to the end of uniform, even and eiicient loom operation irrespective of thenumber of picks per inch.

As the loom operation proceeds and the warp mass diameter of the warp beam 60 decreases owing to consumption of the warp in the Weaving of the fabric, the beam arm 44 which is heavy or weighted falls with d-epletion of the warp mass periphery and thus causes rotation of the tension shaft @13A-and also the entrained tension support arm 484 in a counter-clockwise direction, viewed from Figures 1, 8 and 9. This `action causes angular shifting of the pivotal bearing l to the left or toward the brake drumV 36, thus easing .the tension on the brake band 56 and allowing a freer rotation of the warp beam 60 incident to the L normal pull and tension on the warp by the heddle and other loom action. It will be noted that the movement of the-tension support arm 43 is pivotal about thetension shaft 43 and that there is a secondary pivotal action of the pivotal bearing 5I aboutthe axis of the pivot 50'carried by the tension support arm 48. This may be desirable to preserve alignmentY between the tension rod 52 and the tangent portion of the brake band 56 with which it connects and with which it will normally be held in alignment by the tension ofv the spring 55. This alignment is desirable also to prevent .binding of the tensionrod 52 in the pivotalbearing 5I' because as the tension support arm 48 rotates progressively counter-clockwise,V the tension of the brake band 56 on the spring 55 will be progressively reduced allowing the spring to reactY and expand and increase the distance between the abutments 5| andv 54, the" greater the counter-clockwise rotation of the tension support arm 48. Thus the spring 55 performs a'secondary and a double Afunction in re-V lationto the other parts, namely, ittends to take up--slack in the brake band 56 automatically as the automatic action of the let-off tends to create such slack in the brake band 56. Thereby, the brake blocks 59 are constantly kept in track on the brake drum 36, and moreover, suddenly larg-e and uncontrolled releases, of the brake band 56 are avoided. In other words, the release ofthe' tension of the brake lband 56 on the brake drum 36 is extremely gradual incident to this reactive expansion of the spring 55 in the action of the let-off, which aims to give greater freedom of rotation to the warp beam with the progressive decreases in diameter of the warp mass thereon inV order to compensate for su-ch dierences in diamf eter from full to empty beam throughout the entire gamut of the operation of the loom. It is noted that once the adjustment is made'for ai given'l diameter of warp beam, such adjustment remains-true throughoutthe operation of the loom with subsequent'warp beamspf ,the same' diameter.

ln the eventfofla naw in theweaving auditieV found'necessarytoback down the warp beamlf it will not be necessary to make any mechanical adjustments. In backing down the warp beam 66, the beam gear 35 drives the ratchet pinion 34 in a direction to cause Asliding of the pawls 46 and 41 over the inclined faces of theratchet teeth.

During rotation of the warp beam, the gears 35 and 34 drive the ratchet gear shaft 33 andtherefore also drive the ratchet wheel 31 aiiixed thereto. Such driving, in the normal operation of the loom, is in a counter-clockwise direction, as viewed in Figure 1, so that the notches of the ratchet teeth interlock and engage with the pawls 46 and 41, thus entraining the brake drum 36 to rotate with the warp beam. Consequently, the

rotation of the warp beam in its action of letting.

.Outwardly of the shank 44a, a curved section 44c of the beam arm 44 connects with. the foot 62 which is constructed of a substantial mass ofy material constituting a gravity weight. The straight section 44a of the beam arm is desirable to position the weight 62 carried. by the .curved arm section 44 to a potential position where it may constantly exercise its gravitational force tending at all time to rotate the tension shaft 43 in a counter-clockwise direction, all as permitted by the warp mass diameter of the warp beam.

Referring moreV particularly to Figures 1, 6 and 16, it will be noted that the brake drum 36 has anges 36a, forming an annular depressed track 36 for the cork spacers 59 of the brake band 56, and that such drum 36 is carried by a disk or web 361, having at its central portion a hub 36d which is freely mounted over the ratchet gear shaft 33, being held against axial deviation there- Von by the set thrust collar 39 at one side and the impingement of the boss 36e of the drum disk against the ratchet wheel 31. The set screw 33 binds the ratchet wheel 31 to the ratchet shaft 33 and thus. constitutes the ratchet Wheel 31 as a iixedabutment to take the thrust of theV boss 36e.

, It will be noted, particularly from Figure 6, that the supporting disk 36b is olf center with respect to the brake drum 36 in a direction away from the ratchet wheel 31 whereby to provide within the drum a recess which compactly receives the ratchet wheel 31, the porting disk 36b thus constituting substantially a housing for the ratchet wheel 31 and enabling a close coupled relationship between these conjointly acting parts whereby the ratchet teeth on the peripheral edge of the ratchet wheel 31 rotate concentrically within a central portion of the brake drum 36, which brake drum is thus enabled to perform a second function of acting internally as a support for the Vpawls 46 and 41. As -shown more particularly in Figures 6 and 16, lips 36f extend inwardly from the annulus which is the brake'drum 36 at diametricallyopposite points( and in spaced relation to the disk 361 for the Ypurpose of receiving the pivot pins 15 on which the Vpawls 46 and 41 are mounted. These pawls are associated with springs 16Vto urge the same into the teeth vo1 the ratchet wheel 31. The pawls havegtail pieces brake drum and its sup- 11 projecting circumfererl.vr tallyzaway-.rom thelips Stobefaccessble i9:

9 ratchetwheei arid at the other end itxedly carries the Vpinion 3'!b driven vbythe warp gear 35h.

In the use of this device, the adjustment is all made from the'weavers alley by the simple and single adjustment of the wing nut |03. By rotating this nut in one direction the tension rod |02 is pulled tothe left through the ar-ches 13 and 11| thus drawingvupon the'flexible cable 1| and the adjusting plate 70 to distend the coil spring 98 whereby to put the same under greater tension. This increased tension is transmitted to the brake band 56 by causing the same to moreintimately hug the brake drumand to a greater degree to oppose rotationof the brake drum and consequently of the warp beam. By rotating the nut |03 in the opposite direction the coil spring 98 will be permitted to correspondingly contract drawing down upon the plate 10, the flexible cable 1I and proportionately drawing to the right the tension rod |02 through the arches 13 and 14. In other words, the coil spring 98 will keep the nut |03 tightly against the arch 13 at all times.

Although I have disclosed herein only three modifications of the invention it will be understood that such invention is susceptible of physical embodiment in many dilferent forms and I reserve the right to all such modifications and changes as may come within the scope of the following claims.

I claim:

1. In a loom having a side frame with a warp beam rotatably journaled in said side frame and having a head gear, a friction let-olf comprising a shaft mounted through the side frame and having portions thereof projecting within and to the outside of said frame, a pinion aixed to the inner portion of said shaft and in mesh with said warp beam head gear, a stop member aflxedV to the outer portion of said shaft spaced inwardly of its outer end, a friction drum comprising a drum periphery, a web carrying said periphery and an elongated hub centrally of said web and carrying the same and having an internal smooth bore mounted for free rotation on the outer portion of said shaft with the inner end of said hub abutting said stop, said drum periphery extending outwardly from said web a substantial distance to provide a recess totally within the perimeter of the drum periphery and enclosed only at its inner side by said web, the outer side of said recess being completely open across the entire diameter of the drum periphery, and such open side of the recess exposed outwardly free from said frame, a ratchet wheel having a hub adapted to be slid over the outer free end of said shaft and into said recess, means to -afiix said ratchet wheel hub to said shaft for rotation therewith, pawls pivotally carried by said drum outwardly beyond said ratchet wheel, spring means to urge said pawls into engagement with said ratchet wheel, friction means for engaging the outside surface of said drum periphery, and means for adjusting the tension of said friction means about said drum.

2. A friction let-olf for textile looms as claimed in claim 1 characterized by the fact that the ratchet wheel is a substantially thin disc which is of a diameter to extend in close proximity to the inner surface Vof the drum periphery.

3. A friction let-olf for looms asV claimed in claim 2 further characterized by the fact that the hub of the disc ratchet wheel extends wholly outwardly from the disc to enable the disc to move wholly within the recess and to approach closely the drum web and its hub.

4. A-friction -let-oifzfor textile looms as claimed in` claim Sin which lips on the outer portion of the drum periphery project into the outer portion of the recess and pivot pinsgforthe pawls mounted in the drum Weband in said lips.

5. Ina loom having a side frame with a warp beam rotatably journaled in saidside frame and having a head gear, a friction .let-off comprising a shaft mounted through the side frame and having portions thereofVV projecting within and to the outside of said frame, a pinion afxed to the innen portion of .said rshaft jand inl meshY with said warp beam head gear, a stop member a'xed to the outer portion of said shaft spaced inwardly of its outer end, a friction drum comprising a drum periphery, a web carrying said periphery and an elongated hub centrally of said web and carrying the same and having an internal smooth bore mounted for free rotation on the outer portion of said shaft with the inner end of said hub abutting said stop, said drum periphery extending outwardly from said web a substantial distance to provide a recess totally within the perimeter of the drum periphery and enclosed only at its inner side by said web, the outer side of said recess being completely open across the entire diameter of the drum periphery, and such open side of the recess exposed outwardly free from said frame, a ratchet wheel having a hub adapted to be slid over the outer free end of said shaft and into said recess, means to aiflx said ratchet Wheel hub to said shaft for rotation therewith, pawls pivotally carried by said drum outwardly beyond said ratchet wheel, spring means to urge said pawls into engagement with said ratchet wheel, friction means for engaging the outside surface of said drum periphery, means for adjusting the tension of said friction means about said drum, and warpengaging means, and a common element connecting said warp-engaging means and said tensionadjusting means to which both said means are individually adjustable.

6. The combination of claim 1 further comprising a friction means retainer aixed to the loom side and to one end of said friction means, a long tension rod afiixed to the other end of said friction means, a tension rod support affixed to the loom side through which the tension rod movably passes, and means abutting against said tension rod support for subjecting said tension rod and connected friction means to variable degrees of elastic tension.

7. The combination of claim 1 further comprising a clip for securing one end of said friction means to the motor support bracket of the loom, a helical spring connected to the other end of said friction means, a tension adjusting plate connected to said helical spring, a flexible cable connected to said plate, a tension rod slidable to the loom arches, and means for sliding said rod through said arches.

8. The combination as claimed in 1 characterized by the fact that the friction means comprises a brake band and means for applying tension to said brake band, and means movable in response to diminution of the Warp of the Warp beam for relaxing the tension on the brake band.

9. The combination of claim 5 in which such common element is a rock shaft on which the warp-engaging and the friction-applying means are separately and independently angularly adjustable with means to aiix independently said warp-engaging and friction-applying means for adjustment to said shaft.

' 10;` The" combination ofciami11'furthP'comprising an angulafy azcdju'sirai'f'nl'of` y arm,i a.- pivotal bearing `@ammettby sdrarm, arte'nsion rodi-slid-y abl'e through "saidipivotalf .bering and voonnected. to saidf'brak'efbar; arri? tfthreadedfon said tension rod; ai coil spi-ingom said` rodfbe'ween said nut and pivotal be'aningf; and: means. for progressively rotating' sid arm towzrdsajid drum?.

CHARLTON HDSCN .379311" 1,466,1oo 661,925 Y 13491349 Number 

